WO2003004872A1 - Pompe a piston - Google Patents

Pompe a piston Download PDF

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Publication number
WO2003004872A1
WO2003004872A1 PCT/DE2002/000530 DE0200530W WO03004872A1 WO 2003004872 A1 WO2003004872 A1 WO 2003004872A1 DE 0200530 W DE0200530 W DE 0200530W WO 03004872 A1 WO03004872 A1 WO 03004872A1
Authority
WO
WIPO (PCT)
Prior art keywords
resilient
piston pump
membrane
pump according
pressure chamber
Prior art date
Application number
PCT/DE2002/000530
Other languages
German (de)
English (en)
Inventor
Rene Schepp
Werner-Karl Marquardt
Wolfgang Schuller
Jochen Feinauer
Dirk Foerch
Original Assignee
Robert Bosch Gmbh
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch Gmbh filed Critical Robert Bosch Gmbh
Priority to US10/482,024 priority Critical patent/US7004733B2/en
Priority to JP2003510612A priority patent/JP4051337B2/ja
Priority to DE50207312T priority patent/DE50207312D1/de
Priority to EP02714006A priority patent/EP1404970B1/fr
Publication of WO2003004872A1 publication Critical patent/WO2003004872A1/fr

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
    • B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
    • B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
    • B60T8/40—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition comprising an additional fluid circuit including fluid pressurising means for modifying the pressure of the braking fluid, e.g. including wheel driven pumps for detecting a speed condition, or pumps which are controlled by means independent of the braking system
    • B60T8/4031—Pump units characterised by their construction or mounting
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B11/00—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation
    • F04B11/0008—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using accumulators
    • F04B11/0016—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using accumulators with a fluid spring

Definitions

  • the invention relates to a piston pump according to the preamble of claim 1.
  • the piston pump is provided in particular for a hydraulic, slip-controlled vehicle brake system.
  • the German patent application DE 42 26 646 AI shows a hydraulic vehicle brake system with a pump, in which a pressure damper is provided downstream behind an outlet check valve of the pump. So that the pressure steamer provided in the pressure line has a sufficient effect, the pressure steamer must be of a correspondingly large size. Because of the pressure damper, the known vehicle brake system is built quite large, and an increased manufacturing effort is required. When the brake pedal is actuated, part of the pressure medium displaced via the driver's foot is printed into the pressure damper. Because the pressure damper must be relatively large for a sufficient effect, a relatively large amount of pressure medium must be displaced when the brake pedal is actuated, which must be taken into account by dimensioning the components involved in this process accordingly. As a result, the known brake system builds quite large. Advantages of the invention
  • the piston pump according to the invention with the features of claim 1 has the advantage that the pulsation smoothing device very effectively eliminates the pressure pulsations and pressure waves that otherwise occur in a piston pump. Because of the high effectiveness of the pulsation smoothing device, it can be built quite small and nevertheless one obtains a sufficient effect. Because the pulsation smoothing device can be built quite small, the advantage is obtained that the piston pump is built quite small overall. This has the advantage of an overall small vehicle brake system.
  • the pulsation smoothing device is small due to its good effectiveness, in particular the storage volume can be kept quite small, there is the advantage that when the brake pedal is actuated by the pulsating smoothing device, at most an insignificant part of the pressure medium pressurized by the driver's foot is absorbed, so that the pulsation smoothing device has practically no negative effect on the functioning of the vehicle brake system during actuation of the brake pedal.
  • the pulsation smoothing device is quite small, in particular because the storage volume of the pulsating smoothing device can be kept quite small, it is advantageously also not necessary that a check valve had to be provided downstream of the pulsating smoothing device. Because of this non-necessary check valve, one has the advantage that the manufacturing outlay and the size of the vehicle brake system according to the invention can be kept small; and you get the advantage that the additional check valve, which is not required, cannot be broken either.
  • the elastic, resilient membrane is particularly responsible for higher pressures and high-frequency vibrations and can remove them particularly effectively.
  • the resilient body is particularly responsible for areas with low pressure and for low-frequency vibrations and can suppress them particularly effectively.
  • the piston pump can therefore be designed in such a way that effective pulsation damping and vibration damping are achieved virtually throughout the operation of the piston pump.
  • the elastically resilient membrane which is relatively stiff, but because of its storage in the elastically flexible body, yields even with small pressures and with low-frequency vibrations, the effect of the elastically flexible body is significantly increased, because although with small pressure pulsations and low pressures only the resilient body, but practically hardly the resilient membrane deforms, you still get a relatively wide yield and therefore a relatively large volume change in the pressure chamber in which the pressure pulsations are reduced, even when the pressure is low resilient body itself has only a small overall volume. In other words, even when using an elastically flexible body with a small volume, a relatively large volume change in the pressure chamber and thus an effective damping of vibrations can nevertheless be achieved overall even at low pressures.
  • the drawing shows a section of a hydraulic block of a slip-controlled vehicle brake system in the area of a piston pump of the vehicle brake system.
  • the sectional plane shown is a longitudinal section through the piston pump.
  • FIG. 1 shows a longitudinal section through a preferred, particularly advantageous exemplary embodiment
  • FIG. 2 shows an enlarged detail of a modified exemplary embodiment
  • FIG. 3 shows an enlarged detail of a modified, further exemplary embodiment
  • FIG. 4 shows an enlarged detail of a fourth, modified exemplary embodiment
  • FIG. 6 shows an enlarged section of a sixth, modified exemplary embodiment
  • FIG. 7 shows an enlarged section of a modified, further exemplary embodiment of the piston pump.
  • the piston pump is provided in particular as a pump in a brake system of a vehicle and is used to control the pressure in wheel brake cylinders.
  • ABS or ASR or FDR or EHB are used for such brake systems.
  • the piston pump is used, for example, to return brake fluid from a wheel brake cylinder or from several wheel brake cylinders to a master brake cylinder (ABS) and / or to convey brake fluid from a reservoir into a wheel brake cylinder or into several wheel brake cylinders (ASR or FDR or EHB).
  • the pump is required, for example, in a brake system with wheel slip control (ABS or ASR) and / or in a brake system (FDR) serving as a steering aid and / or in an electro-hydraulic brake system (EHB).
  • the wheel slip control (ABS or ASR) can, for example, prevent the vehicle's wheels from locking during braking when the brake pedal (ABS) is pressed hard and / or the vehicle's driven wheels spinning when the accelerator pedal (ASR) is pressed hard
  • a brake pressure is built up in one or more of the wheel brake cylinders independently of an actuation of the brake pedal or accelerator pedal, for example in order to prevent the vehicle from breaking out of the lane desired by the driver.
  • the pump can also be used in an electrohydraulic brake system (EMS), in which the pump delivers the brake fluid into the wheel brake cylinder or into the wheel brake cylinder if an electric brake pedal sensor detects an actuation of the brake pedal or the pump for filling a reservoir serves the braking system.
  • EMS electrohydraulic brake system
  • FIG. 1 shows a first, particularly advantageous, preferably selected exemplary embodiment.
  • the drawing shows a piston pump 1.
  • the piston pump 1 is installed in a cut-out hydraulic block of the vehicle brake system.
  • Several piston pumps 1 can be installed in the hydraulic block.
  • the hydraulic block forms a pump housing 2 of the piston pump 1.
  • the pump housing 2 consists, for example, of a first body 2.1 fixed to the house, a second body 2.2 fixed to the house, a third body 2.3 fixed to the house, a fourth body 2.4 fixed to the house and a fifth body 2.5 fixed to the house.
  • the first body 2.1 which is fixed to the house, is provided by the hydraulic block of the vehicle brake system educated.
  • the fourth fixed body 2.4 is inserted in the first body 2.1 and serves as a liner.
  • the piston pump 1 comprises the liner inserted in the pump housing 2, an eccentric 6, an inlet connection 8 and an outflow channel 10.
  • the inlet connection 8 and the outlet channel 10 run through the hydraulic block or through the pump housing 2.
  • branching lines (not shown) lead via hydraulic valves (not shown) to a master brake cylinder (not shown) and to wheel brake cylinders (not shown).
  • the fourth body 2.4 which is fixed to the housing and serves as a liner, and a pump piston 14 are inserted into the installation space 12.
  • the pump piston 14, which is displaceably mounted in the pump housing 2 has an end 14a facing the eccentric 6 and an end 14b facing away from the eccentric 6.
  • the pump piston 14 is driven alternately in succession to a suction stroke and a pressure stroke via the eccentric 6.
  • the installation space 12 provided in the pump housing 2 is closed off from the outside by the second body 2.2 which is fixed to the house and serves as a closure piece.
  • the housing-fixed second body 2.2 has an outwardly facing end piece 17.
  • the fourth body 2.4 which serves as a liner, has an end-side liner base 18 facing the housing-fixed second body 2.2.
  • a return spring 19 which rests on the liner base 18 and on the pump piston 14 holds the end 14a of the pump piston 14 in contact with the eccentric 6.
  • the piston pump 1 has an inlet valve 22.
  • the inlet valve 22 has a valve seat 22a, a closing body 22b and a closing spring 22c.
  • the closing spring 22c acts on the closing body 22b against the valve seat 22a provided on the pump piston 14.
  • the piston pump 1 has an outlet valve 24.
  • the outlet valve 24 has a valve seat 24a, a closing body 24b and a closing spring 24c.
  • the closing spring 24c acts on the closing body 24b against the valve seat 24a fixed to the housing, for example provided on the liner bottom 18.
  • One end of the closing spring 24c is supported on the closing body 24a and one end of the closing spring 24c is supported on the third body 2.3 fixed to the housing.
  • the closing spring 24c is realized in the form of a leaf spring 24d.
  • the outer circumference of the leaf spring 24d is supported on the third body 2.3 fixed to the housing.
  • the leaf spring 24d has a hole provided centrally in the leaf spring 24d. This hole centers the closing body 24b in the form of a ball.
  • a passage 25 is provided in the closing spring 24c or a plurality of passages 25 are provided.
  • the at least one passage 25 is preferably dimensioned so large that the passage 25 means practically no throttling for the pressure medium.
  • the at least one passage 25 can also, depending on the requirements of the piston pump 1 and depending on the expediency, be dimensioned so small that the passage 25 means a restriction 25d for the medium flowing through.
  • An inlet passage 26 leads from the inlet connection 8 to the inlet valve 22.
  • a passage 28 leads from the compression space 20 through the liner bottom 18 to the outlet valve 24.
  • the valve seat 24a surrounds the passage 28.
  • the outflow space 30 is the space which adjoins the valve seat 24a downstream.
  • the outflow space 30 is located between the liner base 18 and the leaf spring 24d, which serves more or less as an intermediate wall.
  • the passage 25 connects the outflow space 30 to a pressure chamber 31.
  • a flexible wall 32 is installed in the second body 2.2, which is fixed to the house.
  • the flexible wall 32 separates the pressure chamber 31 from a counter space 36.
  • an easily compressible medium in particular a gas, preferably air.
  • the flexible wall 32 consists of an elastically flexible body 32a and an elastically resilient membrane 32b.
  • the membrane 32b has an outer outer circumference 32c.
  • the resilient body 32a has a circumferential leg 32d facing the pressure chamber 31, a circumferential leg 32e facing the counter space 36 and a back 32f holding the two legs 32d and 32e together. Between the two legs 32d and 32e, the resilient body 32a has a circumferential pocket 32g.
  • the resilient membrane 32b is inserted into the pocket 32g in the region of its outer circumference 32c.
  • the two legs 32d, 32e embrace the outer circumference 32c of the membrane 32b.
  • a countersink 34 is provided in the second body 2.2 fixed to the house.
  • the resilient wall 32 with the body 32a and the membrane 32b is installed in the countersink 34.
  • the resilient body 32a is preferably made of rubber or an elastomer material.
  • the house-fixed third body 2.3 has a gradation, which engages in the countersink 34 in such a way that, in the fully assembled state, the resilient body 32a of the compliant wall 32 is installed in the countersink 34 with pretension.
  • the resilient body 32a is installed with a preload in the axial and radial directions.
  • a connecting duct 38 leads from the outflow chamber 30 into the outflow duct 10.
  • a throttle 39 is provided in the course of the connecting duct 38.
  • the throttle 39 is preferably located directly where the connecting channel 38 discharges the pressure medium from the outflow space 30. In other words, the throttle 39 is preferably very close to the area of the exhaust valve 24.
  • the resilient wall 32 is acted upon by the pressure prevailing in the pressure chamber 31.
  • the pressure in the pressure chamber 31 is essentially the same as the pressure in the outflow space 30.
  • the outflow space 30 is connected to the outflow channel 10 via the throttle 39.
  • the throttle 39 is arranged in the region of the exhaust valve 24 close to the exhaust valve 24. With the help of the throttle 39, it is achieved that the pressure pulsations occurring in the area of the outlet valve 24 act in a concentrated manner on the flexible wall 32 within the pressure chamber 31.
  • the flexible wall 32 prevents pressure pulsations from occurring, directly where the pulsations originated, so that they cannot reproduce beyond the throttle 39 in the outflow channel 10.
  • Components of the pulsation smoothing device 40 are preferably arranged directly in the area of the outlet valve 24.
  • the hydraulic compliance of the pulsation smoothing device 40 can be kept relatively small. This has the advantage that the hydraulic system in the outflow channel 10 can be kept quite stiff downstream of the pulsation smoothing device 40 even without the use of an additional check valve, despite the achievable very good pulsation smoothing.
  • the fixed body 2.2 is installed in a pressure-tight manner in the installation space 12 via a known brothel connection.
  • the body 2.2 seals the high pressure area of the piston pump 1 from the outside.
  • the membrane 32b is preferably a relatively thin plate-shaped disk made of a resilient material, preferably spring steel.
  • the elasticity and resilience of the resilient membrane 32b is dimensioned such that in the case of large pressures and high-frequency pressure pulsations in the pressure chamber 31, in the event of a sudden pressure increase, the membrane 32b yields by bending in the direction of the counter space 36, and in the event of high-frequency sudden pressure drops in the pressure chamber 31 the diaphragm 32b springs back in the direction of the pressure chamber 31. This ensures that even high-frequency pressure pulsations are smoothed in the area immediately behind the valve seat 24a.
  • the leg 32e of the flexible body 32a is compressed, so that there is essentially no further deformation of the leg 32e, but rather a change in volume in the pressure chamber 31 in the case of high-frequency vibrations and high pressures a deflection and thus by deformation of the elastically resilient membrane 32b in the direction of the counter space 36. That is, the membrane 32b is bent in itself in the direction of the counter space 36.
  • the elastically flexible body 32a of the flexible wall 32 also provides a seal between the pressure chamber 31 and the counter space 36, the counter space 36 can be sealed well without the need for an additional component.
  • a circumferential shoulder 41 is formed on the body-fixed body 2.3.
  • the shoulder 41 enables a good chambering of the leg 32d of the elastic body 32a, and the shoulder 41 enables a particularly small structural volume of the piston pump 1.
  • FIG. 2 shows an enlarged detail of a particularly advantageous, preferably selected, modified exemplary embodiment.
  • paragraph 41 is omitted in the exemplary embodiment shown in FIG.
  • the counter space 36 is tightly closed or connected to the atmosphere via a small opening 37 shown in dashed lines in FIG.
  • FIG. 3 shows an enlarged detail of a particularly advantageous, preferably selected, modified, further exemplary embodiment.
  • a circumferential groove 42 is provided on the end face in the countersink 34 provided in the second body 2.2.
  • the groove 42 ensures a reliable reception of the leg 32e of the elastically flexible body 32a.
  • a stop 44 fixed to the housing is provided at the front end of the countersink 34 of the second body 2.2 fixed to the housing.
  • the stop 44 is preferably circumferential and is preferably located in the area where the leg 32e of the flexible body 32a has its inner circumference.
  • the elastically resilient membrane 32b is supported on the stop 44. It is thereby achieved that even at very high pressure in the pressure chamber 31, the leg 32e of the elastically flexible body 32a is protected against excessive compression and thus against overloading.
  • the stop 44 is provided in the vicinity of the outer circumference 32c of the membrane 32b. In the radially inner region of the membrane 32b, the membrane 32b does not touch the stop 44. This ensures that even at high pressures and high frequencies Vibrations the membrane 32b is not hindered by the stop 44. This ensures pulsation damping at every pressure and frequency.
  • FIG. 4 shows an enlarged detail of a particularly advantageous, preferably selected, modified further exemplary embodiment.
  • the elastically resilient membrane 32b is pre-shaped like a pot or hat. This results in a good absorption for the closing spring 24c of the exhaust valve 24, and an improved elasticity of the diaphragm 32b is achieved, which elasticity is even better adapted to the pressures that occur.
  • the outflow space 30 and the pressure chamber 31 can be regarded as a single, contiguous space.
  • three guide ribs 46 leading the closing body 24b are integrally formed on the body 2.3.
  • FIG. 5 shows an enlarged detail of a particularly advantageous, preferably selected, modified further exemplary embodiment.
  • the elastically resilient membrane 32b has a radially inner region 32i and a radially outer, circumferential region 32k. As can be clearly seen in the drawing, the peripheral area 32k is considerably thicker than the inner area 32i of the membrane 32b.
  • the membrane 32b can vibrate well. Because the circumferential, outer Area 32k is quite thick, where the membrane 32b is held in the elastic body 32a, vibration deformations of the membrane 32b are avoided. This contributes to a good seal
  • FIG. 6 shows an enlarged detail of a particularly advantageous, preferably selected, modified further exemplary embodiment.
  • the radially inner region 32 ⁇ of the diaphragm 32b is pre-deformed in the direction of vibration.
  • the ability of the membrane 32b to vibrate can be adapted as required.
  • FIG. 7 shows a section of a further, preferably selected, particularly advantageous exemplary embodiment of the piston pump 1.
  • the elastically resilient body 32a can, for example, also be vulcanized onto the resilient membrane 32b. It is also possible for the resilient membrane 32b to be extrusion-coated with the resilient body 32a.
  • the entire end face of the membrane 32b facing the pressure chamber 31 can be coated with the elastically resilient body 32a.
  • the end face of the membrane 32b facing the pressure chamber 31 has a coating 32m.
  • the coating 32m can optionally also be provided on both end faces of the membrane 32b or only on the end face of the membrane 32b facing the counter space 36.
  • the coating 32m is in one piece with the resilient body 32a and connects the leg 32d without interruption over the entire end face of the membrane 32b. This is between the membrane 32b and the resilient body 32a ensures an absolutely tight seal.

Abstract

Les pompes à piston de systèmes de freinage habituelles occasionnent souvent des problèmes de bruit dus à des pulsations de pression. La pompe à piston (1) de systèmes de freinage selon l'invention comporte au niveau de la soupape d'évacuation (24) une chambre de pression (31), une chambre de contre-pression (36) et une paroi souple (32) séparant la chambre de pression (31) et la chambre de contre-pression (36). Ladite paroi souple (32) contient une membrane élastique (32b) logée dans un corps souple (32a). Ladite pompe à piston est notamment employée dans des systèmes de freinage automobiles avec antipatinage.
PCT/DE2002/000530 2001-06-30 2002-02-15 Pompe a piston WO2003004872A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
US10/482,024 US7004733B2 (en) 2001-06-30 2002-02-15 Piston pump
JP2003510612A JP4051337B2 (ja) 2001-06-30 2002-02-15 ピストンポンプ
DE50207312T DE50207312D1 (de) 2001-06-30 2002-02-15 Kolbenpumpe
EP02714006A EP1404970B1 (fr) 2001-06-30 2002-02-15 Pompe a piston

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10131763 2001-06-30
DE10131763.8 2001-06-30

Publications (1)

Publication Number Publication Date
WO2003004872A1 true WO2003004872A1 (fr) 2003-01-16

Family

ID=7690156

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2002/000530 WO2003004872A1 (fr) 2001-06-30 2002-02-15 Pompe a piston

Country Status (5)

Country Link
US (1) US7004733B2 (fr)
EP (1) EP1404970B1 (fr)
JP (1) JP4051337B2 (fr)
DE (2) DE50207312D1 (fr)
WO (1) WO2003004872A1 (fr)

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2004088137A1 (fr) * 2003-04-02 2004-10-14 Robert Bosch Gmbh Pompe a piston
EP1591659A1 (fr) * 2004-04-27 2005-11-02 Robert Bosch Gmbh Pompe a pistons avec guidage amélioré
WO2008000557A1 (fr) * 2006-06-27 2008-01-03 Robert Bosch Gmbh pompe À piston pour un systÈme de freinage de vÉhicule comprenant un ÉLÉment d'ÉTANCHÉITÉ
WO2008046721A3 (fr) * 2006-10-17 2008-11-06 Bosch Gmbh Robert Pompe à piston pour système de freinage de véhicule, munie d'une tige de piston
WO2009156215A1 (fr) * 2008-06-27 2009-12-30 Robert Bosch Gmbh Pompe à piston d'un système hydraulique de freinage de véhicule
WO2012028362A3 (fr) * 2010-09-02 2012-05-10 Robert Bosch Gmbh Système pour réduire un écoulement de fluide et pompe à piston correspondante pour refouler des fluides
WO2012097901A1 (fr) * 2011-01-21 2012-07-26 Robert Bosch Gmbh Élément élastique et pompe à piston correspondante pour le refoulement de fluides
WO2012152472A1 (fr) * 2011-05-09 2012-11-15 Robert Bosch Gmbh Dispositif d'étranglement d'un écoulement de fluide et pompe à piston correspondante destinée à transporter des fluides
WO2013013865A1 (fr) * 2011-07-27 2013-01-31 Robert Bosch Gmbh Pompe à piston servant au refoulement de fluides et procédé de montage afférent d'une pompe à piston
FR2993941A1 (fr) * 2012-07-25 2014-01-31 Bosch Gmbh Robert Dispositif d'etranglement d'une veine de fluide et pompe a piston ainsi equipee
WO2018146340A1 (fr) * 2017-02-13 2018-08-16 Delphi Technologies Ip Limited Amortisseur

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DE102004035452A1 (de) * 2004-07-22 2006-02-16 Robert Bosch Gmbh Kolbenpumpe mit verbesserter Druckaufbaudynamik
DE102004037147A1 (de) * 2004-07-30 2006-03-23 Robert Bosch Gmbh Kolbenpumpe mit kompakter Haltevorrichtung für eine Rückstellfeder
DE102004061810A1 (de) * 2004-12-22 2006-07-06 Robert Bosch Gmbh Kolbenpumpe mit wenigstens einem Stufenkolbenelement
DE102004063075B4 (de) * 2004-12-28 2015-11-26 Robert Bosch Gmbh Kraftstoff-Hochdruckpumpe für eine Brennkraftmaschine mit einem Stufenkolben und einem Mengensteuerventil
DE102006048903A1 (de) * 2006-10-17 2008-04-30 Robert Bosch Gmbh Pumpe für ein Fahrzeugbremssystem mit einem Ventil
DE102007049152A1 (de) * 2007-10-12 2009-04-16 Robert Bosch Gmbh Hydraulische Kolbenpumpe
KR101404318B1 (ko) * 2007-12-12 2014-06-05 현대모비스 주식회사 댐핑 작용이 부가된 피스톤 펌프 앗세이
DE102008002539A1 (de) * 2008-06-19 2009-12-24 Robert Bosch Gmbh Regelventil für ein Fahrzeugbremssystem und korrespondierendes Fahrzeugbremssystem
BR112012003088B1 (pt) * 2009-08-24 2020-03-03 Kelsey-Hayes Company Sistema de frenagem de veículo
DE102010030342A1 (de) 2010-06-22 2011-12-22 Robert Bosch Gmbh Kolbenpumpe
DE102010030626A1 (de) * 2010-06-29 2011-12-29 Robert Bosch Gmbh Pulsationsdämpferelement für eine Fluidpumpe und zugehörige Fluidpumpe
DE102010039501A1 (de) * 2010-08-19 2012-02-23 Robert Bosch Gmbh Ventil einer Kolbenpumpe mit einem Schließkörper
DE102010040218B4 (de) 2010-09-03 2021-07-22 Robert Bosch Gmbh Dämpfungselement einer Kolbenpumpe
DE102010040193B4 (de) * 2010-09-03 2021-07-22 Robert Bosch Gmbh Kolbenpumpe mit einer Abströmung
DE102010040284A1 (de) * 2010-09-06 2012-03-08 Robert Bosch Gmbh Ventil, insbesondere einer hydraulischen Kolbenpumpe
DE102010063322A1 (de) * 2010-12-17 2012-07-05 Robert Bosch Gmbh Kolbenpumpe mit einer Halterung
DE102010064114B4 (de) * 2010-12-23 2021-07-29 Robert Bosch Gmbh Pumpe mit einer Drossel
DE102013218979A1 (de) * 2013-09-20 2015-04-09 Robert Bosch Gmbh Kolbendämpfer eines Hydraulikaggregats einer Fahrzeugbremsanlage
KR102196190B1 (ko) * 2014-04-10 2020-12-30 주식회사 만도 차량용 전자제어 브레이크 장치의 피스톤 펌프 어셈블리
JP6350805B2 (ja) 2014-05-23 2018-07-04 株式会社アドヴィックス 液圧ダンパ
CN105804987B (zh) * 2016-03-15 2017-06-09 北京航空航天大学 内嵌式液压泵气液混合消振器
CN107816432B (zh) * 2017-09-30 2019-11-19 简式国际汽车设计（北京）有限公司 一种柱塞泵
US11220987B2 (en) * 2017-11-24 2022-01-11 Eagle Industry Co., Ltd. Metal diaphragm damper
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JP7258448B2 (ja) 2018-05-18 2023-04-17 イーグル工業株式会社 ダンパ装置
JP7074563B2 (ja) 2018-05-18 2022-05-24 イーグル工業株式会社 ダンパ装置
US11326568B2 (en) 2018-05-25 2022-05-10 Eagle Industry Co., Ltd. Damper device
DE102019214035A1 (de) * 2019-08-02 2021-02-04 Continental Teves Ag & Co. Ohg Druckkolbengehäuse für eine Druckbereitstellungseinrichtung, Druckbereitstellungseinrichtung und Verfahren zur Montage eines Dämpfungsmittels in einem Druckkolbengehäuse

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2203485A5 (fr) * 1972-10-17 1974-05-10 Guinard Pompes
US4729360A (en) * 1981-05-14 1988-03-08 Robert Bosch Gmbh Damper element
DE4226646A1 (de) 1992-08-12 1994-02-17 Bosch Gmbh Robert Bremsanlage
DE19538615A1 (de) * 1995-10-17 1997-04-24 Teves Gmbh Alfred Hydraulische Bremsanlage mit Pulsationsdämpfer
DE19753909A1 (de) * 1997-11-07 1999-05-12 Itt Mfg Enterprises Inc Schwingungsdämpfer zur Dämpfung von Flüssigkeitsschwingungen in Hydrauliksystemen
US6062830A (en) * 1996-09-03 2000-05-16 Zexel Corporation Diaphragm type damper
DE19928913A1 (de) * 1999-06-24 2001-01-04 Bosch Gmbh Robert Kolbenpumpe

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2371632A (en) * 1943-01-01 1945-03-20 Ideal Roller & Mfg Company Accumulator
DE3152861C2 (de) * 1981-05-14 1983-12-01 Robert Bosch Gmbh, 7000 Stuttgart Dämpferelement
DE10112618A1 (de) * 2001-03-14 2002-09-19 Bosch Gmbh Robert Kolbenpumpe

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2203485A5 (fr) * 1972-10-17 1974-05-10 Guinard Pompes
US4729360A (en) * 1981-05-14 1988-03-08 Robert Bosch Gmbh Damper element
DE4226646A1 (de) 1992-08-12 1994-02-17 Bosch Gmbh Robert Bremsanlage
DE19538615A1 (de) * 1995-10-17 1997-04-24 Teves Gmbh Alfred Hydraulische Bremsanlage mit Pulsationsdämpfer
US6062830A (en) * 1996-09-03 2000-05-16 Zexel Corporation Diaphragm type damper
DE19753909A1 (de) * 1997-11-07 1999-05-12 Itt Mfg Enterprises Inc Schwingungsdämpfer zur Dämpfung von Flüssigkeitsschwingungen in Hydrauliksystemen
DE19928913A1 (de) * 1999-06-24 2001-01-04 Bosch Gmbh Robert Kolbenpumpe

Cited By (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7237474B2 (en) 2003-04-02 2007-07-03 Robert Bosch Gmbh Reciprocating pump
WO2004088137A1 (fr) * 2003-04-02 2004-10-14 Robert Bosch Gmbh Pompe a piston
EP1591659A1 (fr) * 2004-04-27 2005-11-02 Robert Bosch Gmbh Pompe a pistons avec guidage amélioré
US8414276B2 (en) 2006-06-27 2013-04-09 Robert Bosch Gmbh Piston pump for a vehicle brake system with a sealing element
WO2008000557A1 (fr) * 2006-06-27 2008-01-03 Robert Bosch Gmbh pompe À piston pour un systÈme de freinage de vÉhicule comprenant un ÉLÉment d'ÉTANCHÉITÉ
WO2008046721A3 (fr) * 2006-10-17 2008-11-06 Bosch Gmbh Robert Pompe à piston pour système de freinage de véhicule, munie d'une tige de piston
US8388325B2 (en) 2006-10-17 2013-03-05 Robert Bosch Gmbh Piston pump for a vehicle brake system, having a piston rod
CN102066751A (zh) * 2008-06-27 2011-05-18 罗伯特·博世有限公司 汽车液压制动系统的活塞泵
WO2009156215A1 (fr) * 2008-06-27 2009-12-30 Robert Bosch Gmbh Pompe à piston d'un système hydraulique de freinage de véhicule
WO2012028362A3 (fr) * 2010-09-02 2012-05-10 Robert Bosch Gmbh Système pour réduire un écoulement de fluide et pompe à piston correspondante pour refouler des fluides
US9726159B2 (en) 2010-09-02 2017-08-08 Robert Bosch Gmbh Arrangement for throttling a fluid flow, and corresponding piston pump for delivering fluids
US9394898B2 (en) 2011-01-21 2016-07-19 Robert Bosch Gmbh Spring element and corresponding piston pump for delivering fluids
JP2014509373A (ja) * 2011-01-21 2014-04-17 ロベルト・ボッシュ・ゲゼルシャフト・ミト・ベシュレンクテル・ハフツング ばね部材および流体を移送するための対応するピストンポンプ
WO2012097901A1 (fr) * 2011-01-21 2012-07-26 Robert Bosch Gmbh Élément élastique et pompe à piston correspondante pour le refoulement de fluides
WO2012152472A1 (fr) * 2011-05-09 2012-11-15 Robert Bosch Gmbh Dispositif d'étranglement d'un écoulement de fluide et pompe à piston correspondante destinée à transporter des fluides
WO2013013865A1 (fr) * 2011-07-27 2013-01-31 Robert Bosch Gmbh Pompe à piston servant au refoulement de fluides et procédé de montage afférent d'une pompe à piston
US9556859B2 (en) 2011-07-27 2017-01-31 Robert Bosch Gmbh Piston pump for delivering fluids, and corresponding assembly process for a piston pump
FR2993941A1 (fr) * 2012-07-25 2014-01-31 Bosch Gmbh Robert Dispositif d'etranglement d'une veine de fluide et pompe a piston ainsi equipee
WO2018146340A1 (fr) * 2017-02-13 2018-08-16 Delphi Technologies Ip Limited Amortisseur

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DE50207312D1 (de) 2006-08-03
EP1404970A1 (fr) 2004-04-07
DE10229201A1 (de) 2003-01-16
US7004733B2 (en) 2006-02-28
EP1404970B1 (fr) 2006-06-21
JP2004532957A (ja) 2004-10-28
JP4051337B2 (ja) 2008-02-20
US20040234400A1 (en) 2004-11-25

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